Submersible motor pump, motor pump, and tandem mechanical seal

ABSTRACT

A submersible motor pump includes a water jacket having a circulation passage of a coolant, a centrifugal impeller for circulating the coolant, a suction passage configured to provide fluid communication between the circulation passage and a fluid inlet of the centrifugal impeller, and a discharge passage configured to provide fluid communication between a fluid outlet of the centrifugal impeller and the circulation passage. The discharge passage includes a heat-exchange passage formed by two wall surfaces, one of which is constituted by a member which contacts a liquid conveyed by a main impeller. The heat-exchange passage has a circular shape extending radially outwardly from the fluid outlet of the centrifugal impeller. The heat-exchange passage includes at least one axial passage section having a length component in an axial direction of the rotational shaft.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a submersible motor pump having acooling mechanism for a motor.

The present invention also relates to a motor pump for delivering aliquid.

The present invention further relates to a tandem mechanical seal foruse in a submersible motor pump.

2. Description of the Related Art

A submersible motor pump is widely used for delivering a liquid, such assewage, wastewater, or river water, which contains debris and dirttherein. Typically, a motor is disposed above an impeller. Accordingly,under low water level conditions, the pump is operated with the motorexposed in the atmosphere. In order to cool the motor sufficiently evenin such a situation, a water jacket is provided around the motor and aliquid circulates through the water jacket to thereby cool the motor.

Liquids for use in cooling of the motor include a handled liquid of thepump (i.e., a liquid to be conveyed by the pump) and a coolant dedicatedfor the cooling purpose. In the case of using the handled liquid of thepump, the dirt and debris can accumulate in the water jacket or causeclogging of the water jacket. As a result, the need for frequentmaintenance may arise. Therefore, there has been an increasing demandfor the water jacket using the dedicated coolant.

In the case of using the coolant (or cooling liquid), it is necessary toinstall a mechanism for circulating the coolant, in addition to a mainimpeller for delivering the handled liquid. As such a circulatingmechanism, there has been proposed an impeller, which is provided on arotational shaft separately from the main impeller, for circulating thecoolant. The coolant should be isolated sufficiently from the motor andthe handled liquid. Further, the motor should also be separated from thehandled liquid. A tandem mechanical seal, which has two mechanical sealsarranged in series, is conventionally used as a seal mechanism forseparating the motor from the handled liquid. It has also been proposedto provide an impeller of the circulating mechanism between the twomechanical seals. However, the tandem mechanical seal, containing theimpeller therein, has a complex structure. In particular, when using acentrifugal impeller as the impeller for circulating the coolant, it isnecessary to devise structures for assembly.

Further, in the motor cooling mechanism using the coolant, it isnecessary to provide a mechanism for dissipating heat, which has beentransferred from the motor, into the exterior of a circulation passageof the coolant. One of the proposed solutions is to dissipate the heatof the coolant by heat exchange between the coolant and the handledliquid through a pump casing. However, a space between the motor and thepump casing is limited and therefore it is difficult to secure asufficient heat-transfer area for the heat exchange. Further, air pocket(i.e., trapped air) is likely to be created in a housing space of themain impeller (e.g., in a region above the main impeller, in particularin a region behind the main impeller). Such air pocket can hinder theheat exchange between the coolant and the handled liquid. Further, theair pocket also hinders lubrication and cooling of the mechanical seal.As a result, a lifetime of the mechanical seal could be shortened.

SUMMARY OF THE INVENTION

It is therefore a first object of the present invention to provide asubmergible motor pump capable of performing heat exchange effectivelybetween a coolant circulating through a water jacket enclosing a motorand a liquid handled by the pump.

It is a second object of the present invention to provide a motor pumpcapable of quickly and securely expelling air staying at a rear side ofa main impeller for delivering a liquid.

It is a third object of the present invention to provide a tandemmechanical seal having a centrifugal impeller, arranged between twomechanical seals, for circulating a coolant.

The heat exchange between the coolant and the handled liquid isperformed through a heat-exchange member, and the coolant is forced tocirculate by the centrifugal impeller. Therefore, the cooling action bythe coolant is based on forced convection heat transfer. A quantity ofheat in the heat transfer is proportional to a heat transfer area and aheat transfer coefficient. The heat transfer coefficient in forcedconvection heat transfer is expressed by Reynolds number and Prandtlnumber. The higher the velocity of the coolant is, the larger the heattransfer coefficient is, provided that factors determined by physicalproperty of the coolant and the like are eliminated. Therefore, thequantity of heat in the heat transfer can be increased and theefficiency of the heat exchange between the coolant and the handledliquid can be increased by providing a large heat-transfer area and byincreasing flow velocity of the coolant flowing over a heat-transfersurface. In order to increase the flow velocity of the coolant, it isalso useful to provide a narrower passage through which the coolantflows.

In order to achieve the first object of the present invention, oneaspect of the present invention provides a submersible motor pump,including: a water jacket having a circulation passage of a coolant; amotor surrounded by the water jacket; a rotational shaft rotated by themotor; a main impeller secured to the rotational shaft; a centrifugalimpeller for circulating the coolant, the centrifugal impeller beingrotatable together with the rotational shaft; a suction passageconfigured to provide fluid communication between the circulationpassage and a fluid inlet of the centrifugal impeller; and a dischargepassage configured to provide fluid communication between a fluid outletof the centrifugal impeller and the circulation passage. The dischargepassage includes a heat-exchange passage formed by two wall surfacesfacing each other. One of the two wall surfaces is constituted by amember which contacts a liquid conveyed by the main impeller. Theheat-exchange passage has a circular shape extending radially outwardlyfrom the fluid outlet of the centrifugal impeller. The heat-exchangepassage includes at least one axial passage section having a lengthcomponent in an axial direction of the rotational shaft.

In a preferred aspect of the present invention, the axial passagesection further has a length component in a radial direction of thecentrifugal impeller, and the length component in the axial direction islonger than the length component in the radial direction.

In a preferred aspect of the present invention, the heat-exchangepassage further includes at least one radial passage section having onlya length component in a radial direction of the centrifugal impeller.

In a preferred aspect of the present invention, the submergible motorpump further includes guide vanes provided in the radial passagesection.

In a preferred aspect of the present invention, the at least one axialpassage section comprises a first axial passage section and a secondaxial passage section, the at least one radial passage section comprisesa first radial passage section and a second radial passage section, andthe first radial passage section, the first axial passage section, thesecond radial passage section, and the second axial passage section arearranged in this order to provide the heat-exchange passage.

In a preferred aspect of the present invention, the heat-exchangepassage has substantially a constant height over an entire lengththereof.

In a preferred aspect of the present invention, the circulation passagecomprises an outward passage and a return passage which are separated bypartition plates, the discharge passage is connected to an inlet of theoutward passage, an outlet of the outward passage is connected to aninlet of the return passage, and an outlet of the return passage isconnected to the suction passage.

In a preferred aspect of the present invention, a flexible block isdisposed in the water jacket, and a region of a gas contacting thecoolant does not substantially exist in the circulation passage.

In a preferred aspect of the present invention, the flexible blockcomprises a closed-cell foam rubber sponge.

According to the present invention, the centrifugal impeller is employedas an impeller for circulating the coolant. Therefore, pressure of thecoolant can be increased, and as a result the coolant can circulatethrough the narrow passage. Consequently, the flow velocity of thecoolant can be high and the efficiency of the heat exchange can beimproved. Further, because the axial passage section exists, theheat-transfer area can be increased without enlarging the radial size ofthe heat-exchange passage. Furthermore, because swirling flow of thecoolant, formed by the centrifugal impeller, is not destroyed in theheat-exchange passage, the flow velocity of the coolant is kept high andtherefore the efficiency of the heat exchange can be improved.

In order to achieve the second object of the present invention, oneaspect of the present invention provides a motor pump, including: amotor; a rotational shaft rotated by the motor; an impeller secured tothe rotational shaft; and an annular wall arranged above the impeller.The impeller has main blades for pressurizing a liquid and rear vanesfacing the annular wall. The annular wall is shaped so as to separate aspace above the impeller into an inner circumferential space and anouter circumferential space. The annular wall has a return channelthrough which part of the liquid conveyed radially outwardly by the rearvanes is returned to the inner circumferential space.

In a preferred aspect of the present invention, a baffle for disturbingswirling flow of the liquid is provided in the inner circumferentialspace.

In a preferred aspect of the present invention, the annular wall has anupward channel through which part of the liquid conveyed radiallyoutwardly by the rear vanes is directed upwardly from the rear vanes,and the upward channel is in fluid communication with the outercircumferential space.

In a preferred aspect of the present invention, the annular wall forms aheat-exchange passage for performing heat exchange between the liquidand a coolant. The motor pump further includes a water jacketsurrounding the motor, and a circulating mechanism for circulating thecoolant between the water jacket and the heat-exchange passage.

Another aspect of the present invention provides a motor pump,including: a motor; a rotational shaft rotated by the motor; an impellersecured to the rotational shaft; and an annular wall arranged above theimpeller. The impeller has main blades for pressurizing a liquid andrear vanes facing the annular wall. The annular wall is shaped so as toseparate a space above the impeller into an inner circumferential spaceand an outer circumferential space. The annular wall has an upwardchannel through which part of the liquid conveyed radially outwardly bythe rear vanes is directed upwardly from the rear vanes, and the upwardchannel is in fluid communication with the outer circumferential space.

In a preferred aspect of the present invention, the annular wall forms aheat-exchange passage for performing heat exchange between the liquidand a coolant. The motor pump further includes a water jacketsurrounding the motor, and a circulating mechanism for circulating thecoolant between the water jacket and the heat-exchange passage.

According to the present invention, pump action by the rear vanes on therear side of the impeller stirs the air staying in the space above theimpeller together with the liquid, thereby expelling the stagnant air.Further, because the liquid (i.e., the object liquid handled by thepump) is stirred and circulated even after the air is expelled, the heatexchange between the coolant and the liquid is accelerated through theannular wall.

The centrifugal impeller has a fluid outlet having a larger diameterthan that of a fluid inlet thereof, and a liner ring is provided aroundthe fluid inlet. Accordingly, in a case where the centrifugal impelleris arranged in a tandem mechanical seal, it is necessary to insert theliner ring into a space between the centrifugal impeller and amechanical seal at the inlet side of the centrifugal impeller. Since theliner ring has a smaller diameter than that of the mechanical seal, itbecomes difficult to insert the liner ring if the tandem mechanical sealis structured as an integrally assembled unit

In order to achieve the third object of the present invention, oneaspect of the present invention provides a tandem mechanical seal foruse in a rotary machine having a rotational shaft. The tandem mechanicalseal includes: a first seal unit having a first sleeve to be mounted onthe rotational shaft, a first rotary seal ring rotatable together withthe first sleeve, a first stationary seal section contacting the firstrotary seal ring, and a first spring mechanism configured to press thefirst rotary seal ring and the first stationary seal section againsteach other; and a second seal unit having a second sleeve to be mountedon the rotational shaft, a second rotary seal ring rotatable togetherwith the second sleeve, a second stationary seal section contacting thesecond rotary seal ring, a second spring mechanism configured to pressthe second rotary seal ring and the second stationary seal sectionagainst each other, and a centrifugal impeller rotatable together withthe second sleeve. An end surface of the first sleeve and an end surfaceof the second sleeve are brought into contact with each other when thefirst seal unit and the second seal unit are mounted on the rotarymachine. The centrifugal impeller is located between a sealing surfaceof the first seal unit and a sealing surface of the second seal unit.

In a preferred aspect of the present invention, the first seal unitfurther includes a first displacement restriction mechanism configuredto restrict a displacement of the first stationary seal section withrespect to the first sleeve, and the first displacement restrictionmechanism is arranged in a position such that contact between the firstrotary seal ring and the first stationary seal section is maintained bystretch of the first spring mechanism.

In a preferred aspect of the present invention, the first stationaryseal section has a first stationary seal ring contacting the firstrotary seal ring and a first static member to be secured to the rotarymachine.

In a preferred aspect of the present invention, the second springmechanism is located between the second sleeve and the second rotaryseal ring, and the second seal unit further includes a seconddisplacement restriction mechanism configured to couple the secondsleeve and the second rotary seal ring to each other and to restrict adisplacement of the second rotary seal ring with respect to the secondsleeve.

In a preferred aspect of the present invention, the second stationaryseal section has a second stationary seal ring contacting the secondrotary seal ring and a second static member to be secured to the rotarymachine.

In a preferred aspect of the present invention, the first sleeve has afirst positioning surface brought into contact with a first step surfaceformed on the rotational shaft, and the second sleeve has a secondpositioning surface brought into contact with a second step surfaceformed on the rotational shaft.

In a preferred aspect of the present invention, the second springmechanism is provided on a boss of the centrifugal impeller.

According to the present invention, the first sleeve and the secondsleeve are divided and the tandem mechanical seal is constructed by thefirst seal unit and the second seal unit as separate assemblies. Thesefirst seal unit and the second seal unit can be installed individuallyon the rotary machine. Therefore, even when the centrifugal impeller,which has a large diameter and high discharge pressure, is employed, thetandem mechanical seal can be installed in the rotary machine.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view showing a submersible motor pumpaccording to an embodiment of the present invention;

FIG. 2 is a cross-sectional view taken along line A-A in FIG. 1;

FIG. 3 is an enlarged cross-sectional view showing a tandem mechanicalseal and a pump casing shown in FIG. 1;

FIG. 4A is a plan view showing part of a main impeller;

FIG. 4B is a partial cross-sectional view showing the main impeller;

FIG. 5A is a plan view showing a side plate;

FIG. 5B is a bottom view showing the side plate;

FIG. 5C is a cross-sectional view taken along line B-B in FIG. 5B;

FIG. 6A is a plan view showing an inner casing;

FIG. 6B is a cross-sectional view taken along line C-C in FIG. 6A;

FIG. 6C is a bottom view showing the inner casing;

FIG. 7A is a plan view showing an intermediate casing;

FIG. 7B is a bottom view showing the intermediate casing;

FIG. 7C is a cross-sectional view taken along line D-D in FIG. 7B; and

FIG. 8 is an exploded view showing the tandem mechanical seal.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 is a cross-sectional view showing a submersible motor pumpaccording to an embodiment of the present invention. FIG. 2 is across-sectional view taken along line A-A in FIG. 1. A motor shaft and apump shaft are formed integrally to provide a rotational shaft 1. Amotor rotor 3 a is secured to the rotational shaft 1, and a motor stator3 b is arranged so as to surround the motor rotor 3 a. The motor stator3 b is secured to an inner circumferential surface of a cylindricalmotor casing 5. A top cover 6 and a bottom cover 7 are attached to anupper end and a lower end of the motor casing 5, respectively. The motorcasing 5, the top cover 6, and the bottom cover 7 define a hermeticallyclosed space in which the motor rotor 3 a and the motor stator 3 b arehoused to constitute a motor 3.

Bearings 9 are provided on the top cover 6 and the bottom cover 7. Therotational shaft 1 is rotatably supported by these bearings 9. A mainimpeller 12 is secured to an end of the rotational shaft 1. This mainimpeller 12 is housed in a volute casing 19 having a pump suctionopening 19 a and a pump discharge opening 19 b. A tandem mechanical seal90 is provided between the motor 3 and the main impeller 12. This tandemmechanical seal 90 serves to prevent a handled liquid of the pump fromentering the motor 3.

A cylindrical outer cover 8 is provided around the motor casing 5, sothat a space is formed between the motor casing 5 and the outer cover 8.The motor casing 5 and the outer cover 8 constitute a water jacket 11through which a coolant (or cooling liquid) for the motor 3 flows. Thewater jacket 11 is filled with the coolant (which is typicallyanti-freezing solution, such as ethylene glycol solution). The tandemmechanical seal 90 includes a centrifugal impeller 20 which is rotatabletogether with the rotational shaft 1. The coolant is pressurized by therotation of the centrifugal impeller 20. The coolant performs heatexchange with the handled liquid of the pump and is then supplied intothe water jacket 11. After cooling the motor 3 at the water jacket 11,the coolant is retuned to the centrifugal impeller 20 again. In thismanner, the coolant circulates between the centrifugal impeller 20 andthe water jacket 11.

An annular closed-cell foam rubber sponge 21 is fitted into theuppermost portion of the water jacket 11. This rubber sponge 21 isprovided for the following reason. If air exists in the water jacket 11,the air is swallowed up in the flow of the coolant, making the coolantcloudy. As a result the cooling efficiency is lowered to some degree. Onthe other hand, when the water jacket 11 is filled with the coolant, avolume change of the coolant due to a change in temperature thereofcannot be absorbed. Thus, the rubber sponge 21, which is a flexibleblock made of soft material that does not allow the coolant to permeate,is disposed in the water jacket 11. If the water jacket 11 has asufficient cooling capacity, an air layer may be provided instead of theflexible block, because the cloudy coolant does not cause a greatdecrease in the cooling efficiency.

As shown in FIG. 2, four vertically extending ribs 5 a are provided onan outer circumferential surface of the motor casing 5. Further, fourpartition plates 23, which partition the interior space of the waterjacket 11 in a circumferential direction, are mounted on the four ribs 5a, respectively. An inner circumferential surface of the outer cover 8and the partition plates 23 may not be in contact. The partition plates23 extend vertically from the lower end of the water jacket 11 to apredetermined position to form four circulation passages 24A, 24B, 24C,and 24D in the water jacket 11. Two of the four circulation passagesprovide outward passages (indicated by reference numerals 24A and 24B)of the coolant, and the other two provide return passages (indicated byreference numerals 24C and 24D) of the coolant. The arrangement of theoutward passages 24A and 24B is axisymmetric, and the arrangement of theoutward passages 24C and 24D is also axisymmetric.

Cooling of the motor 3 is performed by the heat exchange between thecoolant flowing through the water jacket 11 and the motor 3 through themotor casing 5. The temperature of the coolant is increased aftercooling the motor 3. Therefore, if the coolant itself cannot be cooled,the motor 3 could be overheated. It is possible to release heat throughthe outer cover 8 into the environment around the water jacket 11.However, when the outer cover 8 is exposed in the atmosphere, sufficientrelease of heat cannot be expected. Therefore, it is preferable toperform sufficient release of heat via heat exchange between the coolantand the handled liquid of the pump, as discussed below.

Mixing of the coolant and the handled liquid should be avoided.Therefore, the heat exchange between the coolant and the handled liquidis performed through a certain member (i.e., a heat-exchange member).That is, in the heat exchange between the coolant and the handledliquid, the heat transfer coefficient between the heat-exchange memberand the coolant and handled liquid is important. Generally, a quantityof heat transferred between a fluid and an object becomes larger as heattransfer area becomes larger, and the heat transfer coefficient becomeslarger as the flow velocity of the fluid becomes higher. When the fluidflows through a narrow passage, the flow velocity increases, but on theother hand a resistance of the passage becomes greater and as a resultpressure loss becomes larger. Therefore, it is preferable to use, as thecirculation impeller for the coolant, a centrifugal impeller that canrealize a high head with respect to flow rate. In order to furtherincrease the efficiency, it is preferable to use a closed-typecentrifugal impeller.

The centrifugal impeller 20 for circulating the coolant is incorporatedin the tandem mechanical seal 90. This tandem mechanical seal 90 ishoused in a pump casing that is constituted by a side plate 30, an innercasing 50, and an intermediate casing 60. The intermediate casing 60 issecured to lower portions of the bottom cover 7 and the outer cover 8.The inner casing 50 and the side plate 30 are secured to a lower portionof the intermediate casing 60 by bolts 45 and 46. The inner casing 50 isdisposed above the side plate 30. The volute casing 19 is secured to thelower portion of the intermediate casing 60. A housing space of the mainimpeller 12 is formed by the side plate 30 and the volute casing 19.

FIG. 3 is an enlarged cross-sectional view showing the tandem mechanicalseal and the pump casing shown in FIG. 1. As shown in FIG. 3, in thisembodiment, a closed-type centrifugal impeller 20 is used as thecirculation impeller for the coolant. This centrifugal impeller 20 isinterposed between the inner casing 50 and the side plate 30. Aheat-exchange passage 80, extending in a disk shape, is provided betweenthe inner casing 50 and the side plate 30. More specifically, theheat-exchange passage 80 is formed by a lower surface of the innercasing 50 and an upper surface of the side plate 30. This heat-exchangepassage 80 extends radially outwardly from a fluid outlet of thecentrifugal impeller 20, and has a circular shape as viewed from anaxial direction. The fluid outlet of the centrifugal impeller 20 facesan inlet of the heat-exchange passage 80, so that the coolant,discharged from the centrifugal impeller 20, flows into theheat-exchange passage 80. Distance between the lower surface of theinner casing 50 and the upper surface of the side plate 30, whichconstitute wall surfaces of the heat-exchange passage 80, is small andis substantially constant throughout the heat-exchange passage 80 in itsentirety. Therefore, a cross section of the heat-exchange passage 80only expands with a radial position, and a height of the heat-exchangepassage 80 is substantially constant over the entire length thereof.

The heat-exchange passage 80 includes an inner horizontal passage (afirst radial passage section) 81 surrounding the centrifugal impeller20, an inner axial passage (a first axial passage section) 82 connectedto the inner horizontal passage 81, an outer horizontal passage (asecond radial passage section) 83 connected to the inner axial passage82, and an outer axial passage (a second axial passage section) 84connected to the outer horizontal passage 83. The inner horizontalpassage 81 has a flat annular shape extending radially outwardly fromthe centrifugal impeller 20. The inner axial passage 82 extends axiallyfrom the inner horizontal passage 81 toward the main impeller 12 whileextending radially outwardly to have an approximately truncated coneshape as a whole. The outer horizontal passage 83 has a flat annularshape extending radially outwardly from the inner axial passage 82. Theouter axial passage 84 extends axially from the outer horizontal passage83 toward the motor 3 to have an approximately cylindrical shape as awhole.

The inner axial passage 82 has both a length in the axial direction anda length in the radial direction, and the axial length is longer thanthe radial length. The inner axial passage 82 has the length in theradial direction for the following reasons. The first reason is toreduce pressure loss caused by a great change in the flow direction(i.e., from the radial direction to the axial direction) of the coolantwith large kinetic energy immediately after the coolant is dischargedfrom the centrifugal impeller 20. The second reason is that, if theinner axial passage 82 has only the length in the axial direction, aninterior space (indicated by reference numeral 41) of the side plate 30adjacent to the inner axial passage 82 becomes small and the handledliquid is likely to stay in this space.

The coolant, pressurized by the centrifugal impeller 20, has a velocitycomponent in a swirling direction. By not disturbing this swirling flow,relative velocity between the side plate 30 (i.e., the heat-exchangemember) and the coolant can be kept high. Further, the heat-exchangepassage 80 includes the axial passage section which extendssubstantially in the axial direction. In such axial passage section, thecross-sectional area of the passage hardly increases. Therefore, theaxial passage section of the heat-exchange passage 80 can prevent thedecrease in the velocity of the coolant while maintaining a largeheat-transfer area. Although a maximum radius of the heat-exchangepassage 80 that can be used for the heat exchange is limited by thediameter of the main impeller 12 or the diameter of the motor 3, theheat-exchange passage 80 can be made long by providing the axiallyextending passage.

FIG. 4A is a plan view showing part of the main impeller, and FIG. 4B isa partial cross-sectional view showing the main impeller. The mainimpeller 12 includes a plurality of main blades 13 for pressurizing theliquid. The main impeller 12 is disposed such that the main blades 13face the pump suction opening 19a (see FIG. 1). A plurality of rearvanes 14 are provided on a rear surface (an upper surface) of the mainimpeller 12. More specifically, radially extending grooves 15 are formedon the rear surface of the main impeller 12, and the rear vanes 14 areformed between these grooves 15. The rear vanes 14 are arranged aroundthe center of the main impeller 12 at equal intervals, and are disposedso as to face the side plate (annular wall) 30, as shown in FIG. 3. Therear vanes 14 rotate together with the main impeller 12 to stir andcirculate the liquid existing around the side plate 30, thus preventingreduction of the efficiency of the heat exchange. In this embodiment,the main impeller 12 is described as an impeller constituting a volutetype mixed flow pump. However, the main impeller 12 is not limited tothis example.

FIG. 5A is a plan view showing the side plate (annular wall), FIG. 5B isa bottom view showing the side plate, and FIG. 5C is a cross-sectionalview taken along line B-B in FIG. 5B. The side plate (an annular wall)30 has a substantially annular shape. The heat-exchange passage 80 isformed on the upper surface of the side plate 30, and the handled liquidcontacts a lower surface of the side plate 30. This side plate 30 servesas the heat-exchange member for performing the heat exchange between thecoolant and the handled liquid. It is preferable that the side plate 30be made of material having a high thermal conductivity, such as bronzeor brass. The side plate 30 is secured to the intermediate casing 60with the bolts 46. No components, other than a first stationary sealsection of the tandem mechanical seal 90, are secured to the side plate30. Therefore, material and shape that exhibit relatively low strengthare permitted to be used for the side plate 30, because the side plate30 is not required to support heavy components, such as the motor 3 orthe volute casing 19.

Inner guide vanes 31 and outer guide vanes 32 are provided on the uppersurface of the side plate 30. The inner guide vanes 31 are located inthe inner horizontal passage 81, and the outer guide vanes 32 arelocated in the outer horizontal passage 83. The inner guide vanes 31 andthe outer guide vanes 32 are provided for the purpose of conditioningthe flow of the coolant. As shown in FIG. 5A, an angle of the innerguide vanes 31 with respect to a tangential direction of a virtualcircle (not shown in the drawing) that is concentric with the rotationalshaft 1 is smaller than an angle of the outer guide vanes 32 withrespect to the above tangential direction, so that the inner guide vanes31 do not disturb the swirling component of the coolant.

The upper surface (front surface) of the side plate (annular wall) 30contacts the coolant, while the lower surface (rear surface) of the sideplate 30 contacts the handled liquid. A vertical extension wall 33having a cylindrical shape and extending toward the main impeller 12 isformed on the lower surface of the side plate 30. Further, a horizontalextension wall 34 extending radially inwardly from a lower end of thevertical extension wall 33 is provided. These extension walls 33 and 34serve to increase a contact area between the handled liquid and the sideplate 30, i.e., the heat transfer area. The horizontal extension wall 34is arranged so as to face the rear vanes 14. The side plate (annularwall) 30 partitions a space above the main impeller 12 into an innercircumferential space 41 and an outer circumferential space 42, as shownin FIG. 1 and FIG. 3.

The vertical extension wall 33 has inwardly recessed portions, whichform recesses 35. These recesses 35 provide upward channels that leadpart of the liquid, delivered radially outwardly by the rear vanes 14,upwardly from the rear vanes 14. The recesses 35 face the rear vanes 14and the outer circumferential space 42. Inner ends of the recesses 35lie radially outwardly of inner ends of the rear vanes 14 facing therecesses 35. Therefore, the liquid, pressurized by the rear vanes 14, issupplied to the recesses 35. This pressurized liquid ascends from therear vanes 14 through the recesses 35 to flow on the outercircumferential surface of the side plate 30. This flow of the liquidstirs and circulates the liquid in the outer circumferential space 42located at the back side of the main impeller 12.

The horizontal extension wall 34 has through-holes 36 formed therein.These through-holes 36 provide return channels that lead part of theliquid, delivered radially outwardly by the rear vanes 14, back to theinner circumferential space 41. Inner ends of the through-holes 36 lieradially outwardly of the inner ends of the rear vanes 14 facing thethrough-holes 36. Therefore, the liquid, pressurized by the rear vanes14, is supplied to the through-holes 36. This pressurized liquid flowsin the axial direction of the rotational shaft 1 to stir and circulatethe liquid in the inner circumferential space 41 located at the backside of the main impeller 12. This flow of the liquid has a swirlingcomponent. This swirling flow is disturbed by a plurality of baffles(ribs) 37 provided on the lower surface of the side plate 30, wherebyagitation of the liquid is further promoted. These baffles 37 areconfigured as vertical walls projecting radially inwardly.

Such stirring action and circulating action of the handled liquidprevent stagnation of the handled liquid that is used for the heatexchange with the side plate 30, thus improving the heat exchangeefficiency. Air pocket is likely to be created in top regions of theinner circumferential space 41 and the outer circumferential space 42,particularly at the time of starting the operation of the pump. Thepresence of the air in these spaces not only lowers the heat exchangeefficiency, but also adversely affects lubrication of the mechanicalseal. According to the embodiment as described above, the rear vanes 14,the through-holes 36, the recesses 35, and the baffles 37 can stir theliquid in the spaces 41 and 42, so that the flow of the liquid can expelthe trapped air from these spaces. While the submersible motor pump isdescribed in this embodiment, structures for effectively expelling theair staying in the space behind the main impeller 12 can be applied toother types of pumps.

FIG. 6A is a plan view showing the inner casing, FIG. 6B is across-sectional view taken along line C-C in FIG. 6A, and FIG. 6C is abottom view showing the inner casing. The inner casing 50 has anapproximately annular shape. Radially extending ribs 51 are provided onan upper surface of the inner casing 50. The rear surface (i.e., thelower surface) of the inner casing 50 forms, together with the sideplate 30, the heat-exchange passage 80. An inner circumferential edge 52of the inner casing 50 serves as a liner ring (or casing ring) for thecentrifugal impeller 20. That is, the upper opening of the inner casing50 constitutes a suction opening of the circulation pump for thecoolant.

FIG. 7A is a plan view showing the intermediate casing, FIG. 7B is abottom view showing the intermediate casing, and FIG. 7C is across-sectional view taken along line D-D in FIG. 7B. An upper surfaceof the intermediate casing 60 has four openings (i.e., two entrances 61Aand 61B, and two exits 61C and 61D). These openings 61A, 61B, 61C, and61D are arranged at equal intervals along the circumferential direction.The entrances 61A and 61B are connected to the return passages 24C and24D of the water jacket 11, respectively, and the exits 61C and 61D areconnected to the outward passages 24A and 24B of the water jacket 11,respectively. The two entrances 61A and 61B are in fluid communicationwith a housing space 64, located in a center of a lower portion of theintermediate casing 60, through two inlet passages (suction passages) 62penetrating vertically through the intermediate casing 60. In thehousing space 64, the mechanical seal 90 and the centrifugal impeller 20are disposed. The two exits 61C and 61D are in fluid communication withtwo coolant outlets 65, respectively, through two outlet passages 63penetrating vertically through the intermediate casing 60. The coolantoutlets 65 are formed in the lower surface of the intermediate casing60.

As indicated by dotted lines in FIG. 7B, the inlet passages 62 and theoutlet passages 63 of the intermediate casing 60 are separated by twopartition walls 66, so that these passages 62 and 63 do not communicatewith each other. The two inlet passages 62 are in fluid communicationwith each other through the housing space 64, while the two outletpassages 63 are not in fluid communication with each other and areprovided as separate passages. The two coolant outlets 65 are connectedto part of the end of the heat-exchange passage 80, so that the coolantthat has been cooled by the handled liquid flows through the outletpassages 63 into the water jacket 11. Therefore, the heat-exchangepassage 80 and the outlet passages 63 constitute a discharge passagethat provides fluid communication between the centrifugal impeller 20and the water jacket 11.

The end of the heat-exchange passage 80 is connected to the outletpassages 63 formed in the intermediate casing 60. The end of theheat-exchange passage 80 has an annular shape, while the outlet passages63 are constituted by two of the four passages passing through theintermediate casing 60 in the axial direction, as described above. Theoutlet passages 63 are connected to the two axisymmetric outwardpassages 24A and 24B of the water jacket 11. The coolant flows throughthe outward passages 24A and 24B in the axial direction to cool themotor 3, impinges on the rubber sponge 21 to change its flow direction,and descends in the neighboring return passages 24C and 24D. Theaxisymmetric two return passages 24C and 24D are connected to the twoinlet passages 62 (which are the other two of the four passages passingthrough the intermediate casing 60 in the axial direction),respectively, so that the coolant is led to the suction inlet of thecentrifugal impeller 20. In this manner, the coolant circulates throughthe centrifugal impeller 20, the heat-exchange passage 80, the outletpassages 63, the water jacket 11 (the outward passages 24A and 24B andthe return passages 24C and 24D), the inlet passages 62, and thecentrifugal impeller 20.

FIG. 8 is an exploded view showing the tandem mechanical seal. Thetandem mechanical seal 90 according to the present embodiment includes afirst seal unit 100 having no centrifugal impeller and a second sealunit 120 having the centrifugal impeller 20. The first seal unit 100 andthe second seal unit 120 are constructed as independent assemblies whichcan be separated from each other.

The first seal unit 100 includes, as rotary elements, a first sleeve 102secured to the rotational shaft 1, and a first rotary seal ring 104which is rotatable together with the first sleeve 102 through a pin 103.An O-ring 106 is disposed between the first sleeve 102 and the firstrotary seal ring 104. The first seal unit 100 further includes, asstationary elements, a first static member 107 secured to the side plate30 (which is a frame body of a rotary machine), a first stationary sealring 109 supported by the first static member 107 through an O-ring 108,and springs 110 configured to press the first stationary seal ring 109against the first rotary seal ring 104. The springs 110 are arrangedbetween the first static member 107 and the first stationary seal ring109. The first stationary seal ring 109 and the first static member 107engage each other through engagement members 111, so that the firststationary seal ring 109 does not rotate. In this embodiment, the firststationary seal ring 109 and the first static member 107 constitute afirst stationary seal section.

The first static member 107, the first rotary seal ring 104, and thefirst stationary seal ring 109 are arranged so as to surround the firstsleeve 102. A snap ring 115 for restricting a displacement of the firststatic member 107 with respect to the first sleeve 102 caused by thesprings 110 is provided on an outer circumferential surface of the firstsleeve 102. The position of the snap ring 115 on the first sleeve 102 issuch that the springs 110 do not stretch to their full length and thefirst stationary seal ring 109 and the first static member 107 do notdisengage. This snap ring 115 can allow the first seal unit 100 tomaintain its integrally assembled state even when the first seal unit100 is not installed on the rotary machine. Therefore, the first sealunit 100 can be mounted on the pump simply by securing the first staticmember 107 to the frame body (i.e., the side plate 30). In particular,because positioning of the engagement members 111 and the pin 103 can becompleted before the first seal unit 100 is mounted on the pump, theassembly of the pump can be facilitated.

The second seal unit 120 includes, as stationary elements, a secondstatic member 121 secured to the intermediate casing 60 (i.e., a framebody of the rotary machine), and a second stationary seal ring 123supported by the second static member 121 through an O-ring 122. Thesecond stationary seal ring 123 engages the second static member 121through engagement members 124 so as not to rotate. In this embodiment,the second stationary seal ring 123 and the second static member 121constitute a second stationary seal section. The second seal unit 120further includes, as rotary elements, a second sleeve 131 secured to therotational shaft 1, a second rotary seal ring 132 which is rotatabletogether with the second sleeve 131, and springs 133 configured to pressthe second rotary seal ring 132 against the second stationary seal ring123. An O-ring 134 is disposed between the second sleeve 131 and thesecond rotary seal ring 132.

The second rotary seal ring 132 is coupled to the second sleeve 131 withbolts 136. These bolts 136 are secured to the second rotary seal ring132 and engage the second sleeve 131 loosely. The second rotary sealring 132 and the bolts 136 are movable in the axial direction relativeto the second sleeve 131. The bolts 136 serve as stopper for restrictinga displacement of the second rotary seal ring 132 with respect to thesecond sleeve 131.

The centrifugal impeller 20 is formed integrally on an outercircumferential surface of the second sleeve 131. The centrifugalimpeller 20 is arranged with its fluid inlet facing the second staticmember 121. The centrifugal impeller 20 is located between a sealingsurface (i.e., contact surface between the first rotary seal ring 104and the first stationary seal ring 109) of the first seal unit 100 and asealing surface (i.e., contact surface between the second rotary sealring 132 and the second stationary seal ring 123) of the second sealunit 120. The springs 133 are provided on a boss of the centrifugalimpeller 20. The displacement of the second rotary seal ring 132 by thestretch of the springs 133 is limited by the bolts 136. Therefore, evenwhen the rotary elements are not mounted on the rotary machine, therotary elements can maintain an integrally assembled state. Further,because the first sleeve 102 and the second sleeve 131 are constructedas separate components, the first seal unit 100 and the second seal unit120 can be separated as independent assemblies.

Procedures for installing the tandem mechanical seal 90 in the rotarymachine are as follows:

1. The stationary elements of the second seal unit 120 are secured tothe intermediate casing 60 with the bolts 55 (see FIG. 3).

2. The inner casing 50 is secured to the intermediate casing 60 with thebolts 45 (see FIG. 1).

3. A key 140 (see FIG. 3) is attached to the rotational shaft 1, and therotary elements of the second seal unit 120 are mounted on therotational shaft 1.

4. The side plate 30 is secured to the intermediate casing 60 with thebolts 46 (see FIG.

1).

5. A pin 141 (see FIG. 3) is attached to the rotational shaft 1, and thefirst seal unit 100 is secured to the side plate 30 with the bolts 56(see FIG. 3).

6. The main impeller 12 is secured to the rotational shaft 1 with a bolt47 (see FIG. 1).

When the main impeller 12 is mounted on the rotational shaft 1, thefirst seal unit 100 and the second seal unit 120 are biased upwardly inFIG. 3 to cause the springs 110 and 133 to contract. As shown in FIG. 8,a lower portion of the first sleeve 102 is a small-diameter portion 102a, whose upper end surface (a first positioning surface) 105 contacts afirst step surface 1 a of the rotational shaft 1, as shown in FIG. 3. Anupper end of the first sleeve 102 contacts a lower end of the secondsleeve 131. Further, an upper end surface (a second positioning surface)135 of the second sleeve 131 contacts a second step surface 1 b of therotational shaft 1. In this manner, positioning of the first sleeve 102and the second sleeve 131 is accomplished. Torque of the rotationalshaft 1 is transmitted to the first sleeve 102 and the second sleeve 131via the pin 141 and the key 140, which serve as torque transmissionmembers, respectively.

The closed-type centrifugal impeller 20 requires installation of a linerring. As can be seen from FIG. 3, since the fluid inlet of thecentrifugal impeller 20 has a small diameter, the liner ring should beplaced at a position between the second static member 121 and thecentrifugal impeller 20. In the present embodiment, the second seal unit120 is constructed by two independent assemblies, i.e., the stationaryelements and the rotary elements, and these two assemblies are mountedon the rotary machine individually. Therefore, a small-diameter linerring can be disposed between the stationary elements and the centrifugalimpeller 20.

Further, because the first sleeve 102 and the second sleeve 131 areprovided as separate components so that the first seal unit 100 and thesecond seal unit 120 can be separated, a frame body of the pump (e.g.,the side plate 30 in this example) can be inserted even in a spacesandwiched between the first static member 107 of the first seal unit100 and the centrifugal impeller 20. With these configurations, anoutside diameter of the mechanical seal can be made small. Furthermore,because the side plate 30, which is made of material having a highthermal conductivity, can be inserted into a space located inwardly ofthe fluid outlet of the centrifugal impeller 20, the heat exchangebetween the high-velocity coolant just discharged from the impeller 20and the handled liquid can be performed securely through the side plate30.

The previous description of embodiments is provided to enable a personskilled in the art to make and use the present invention. Moreover,various modifications to these embodiments will be readily apparent tothose skilled in the art, and the generic principles and specificexamples defined herein may be applied to other embodiments. Therefore,the present invention is not intended to be limited to the embodimentsdescribed herein but is to be accorded the widest scope as defined bylimitation of the claims and equivalents.

1-15. (canceled)
 16. A tandem mechanical seal for use in a rotarymachine having a rotational shaft, comprising: a first seal unit havinga first sleeve to be mounted on the rotational shaft, a first rotaryseal ring rotatable together with said first sleeve, a first stationaryseal section contacting said first rotary seal ring, and a first springmechanism configured to press said first rotary seal ring and said firststationary seal section against each other; and a second seal unithaving a second sleeve to be mounted on the rotational shaft, a secondrotary seal ring rotatable together with said second sleeve, a secondstationary seal section contacting said second rotary seal ring, asecond spring mechanism configured to press said second rotary seal ringand said second stationary seal section against each other, and acentrifugal impeller rotatable together with said second sleeve, whereinan end surface of said first sleeve and an end surface of said secondsleeve are brought into contact with each other when said first sealunit and said second seal unit are mounted on the rotary machine, andwherein said centrifugal impeller is located between a sealing surfaceof said first seal unit and a sealing surface of said second seal unit.17. The tandem mechanical seal according to claim 16, wherein said firstseal unit further includes a first displacement restriction mechanismconfigured to restrict a displacement of said first stationary sealsection with respect to said first sleeve, and said first displacementrestriction mechanism is arranged in a position such that contactbetween said first rotary seal ring and said first stationary sealsection is maintained by stretch of said first spring mechanism.
 18. Thetandem mechanical seal according to claim 16, wherein said firststationary seal section has a first stationary seal ring contacting saidfirst rotary seal ring and a first static member to be secured to therotary machine.
 19. The tandem mechanical seal according to claim 16,wherein: said second spring mechanism is located between said secondsleeve and said second rotary seal ring; and said second seal unitfurther includes a second displacement restriction mechanism configuredto couple said second sleeve and said second rotary seal ring to eachother and to restrict a displacement of said second rotary seal ringwith respect to said second sleeve.
 20. The tandem mechanical sealaccording to claim 16, wherein said second stationary seal section has asecond stationary seal ring contacting said second rotary seal ring anda second static member to be secured to the rotary machine.
 21. Thetandem mechanical seal according to claim 16, wherein: said first sleevehas a first positioning surface brought into contact with a first stepsurface formed on the rotational shaft; and said second sleeve has asecond positioning surface brought into contact with a second stepsurface formed on the rotational shaft.
 22. The tandem mechanical sealaccording to claim 16, wherein said second spring mechanism is providedon a boss of said centrifugal impeller.